Universal thermal actuator and hybrid high integrity pressure protection systems

ABSTRACT

This invention relates to an universal thermal actuation imbedded in Hybrid High Integrity Pressure Protection System (H-HIPPS) for critical services in pipelines, refiners, power plants and subsea, the hybrid system includes a quick isolation subsystem between an overpressure zone and a normal pressure zone and a quick releasing subsystem between the overpressure zone and a lower pressure zone with quadruple redundancies, more particularly, the universal thermal actuation subsystem based on thermodynamics has a thermal system (pressure sources, volume vessel like air return reservoir and heat source) and a control chamber and shutter valves, the isolation subsystem system controlled by the actuation system has one normal open valve, the releasing subsystem system controlled by the actuation system has one normal closed valve, the actuation systems can be used for both linear and rotary actuation applications anywhere either remote locations or subsea.

CROSS-REFERENCE TO RELATED APPLICATION

This application claims the benefit of provisional patent application Ser. No. 62/671,989 filed on May 15, 2018 by the present inventor.

FEDERALLY SPONSORED RESEARCH

No

SEQUENCE LISTING OR PROGRAM

No

BACKGROUND

This invention relates to an universal thermal actuation subsystem imbedded in Hybrid High Integrity Pressure Protection System (H-HIPPS) for critical services in pipelines, refiners, power plants and subsea, the hybrid system includes a quick isolation subsystem between an overpressure zone and a normal pressure zone and a quick releasing subsystem between the overpressure zone and a lower pressure zone with quadruple redundancies, more particularly, the universal thermal actuation subsystem based on thermodynamics has a thermal system (pressure sources, volume vessel and heat source) and a control chamber and actuators, the isolation subsystem system controlled by the actuation system has at least one normal open valve for isolating over pressurize fluids, the releasing subsystem system controlled by the actuation system has at least one normal closed valve and one normal closed valve for releasing over pressurize fluids, the actuation systems is used for both linear and rotary applications even without any electric power and electric signal or external power supply or subsea for emergence actions.

In 1988, Piper Alpha platform fire accident killed 167 people and costed $3.4 billion because of removing the Pump A's pressure safety valve, in 1999, a pressure relief valve failed on a 16-inch gasoline pipeline operated by the Olympic Pipe Line Company in Bellingham, Wash., spilling 277,000 gallons of gasoline into the river, as results the gasoline exploded, killing three young boys, the incident resulted in five felony convictions for Olympic employees and a $75 million wrongful death settlement, in 2010, Deepwater Horizon oil spill During the Deepwater Horizon drilling rig explosion incident on Apr. 20, 2010, the blowout preventer (BOP) should have been activated automatically, cutting the drill string and sealing the well to preclude a blowout and subsequent oil spill in the Gulf of Mexico, but it failed to fully engage. Underwater robots (ROVs) later were used to manually trigger the blind shear ram preventer, to no avail, but the blow off preventer failed to active, the U.S. government estimated the total discharge at 4.9 million barrels, there are numerous pipeline leak or explosion accidents in last 30 years reported by EPA, City Lab daily and other organizations.

Today there are two dependent solutions in the market for the overpressure problem (1) to block the overpressure fluid or fire fluid zone into a normal pressure zone (2) to release the overpressure fluid or fired fluid into a low pressure zone or safety tank, as far as the BOP reliable actuation control system is concerned, there is no solution.

With current HIPPS, the overpressure protection is achieved by reducing the risk of overpressure fluid to a tolerable degree. HIPPS design is governed by: IEC 61508: “Functional Safety of Electrical/Electronic/Programmable Electronic Safety Related Systems” IEC 61511: “Functional Safety: Safety Instrumented Systems for the Process Sector,” ANSI/ISA S84.01-1996, “Application of Safety Instrumented Systems (SIS) for the Process Industry,” API 170 Recommended Practice for Subsea High Pressure Protection Systems (HIPPS) In most cases, the HIPPS is equipped with two over pressure rating shut off valves, two actuators and pressure transmitters and a feedback control system, but this subsystem at this point is just a combination of conventional parts like two ball valves, two actuators and two pressure sensors and controller and is constructed under overpressure class at least two or three time in overpressure fluid zone even for a short period time and waste lot of materials and capacity in normal pressure conditions, this system has high cost and only acts at components level, so far there is no single valve or actuator, which are developed for a high integrity, seamless pressure protection system, as far as the validation test for the system, the current method is the partial stroke test, but it does not address the critical points like closed positions where the operation torque and forces would increase dramatically and the valve and the actuations could fail even they pass the partial stroke tests, moreover, for the valves, what is the pressure rating of the valve for surge pressure? What is the power redundancy for pressure sensors if the power supply is off?

The conventional releasing subsystem is constructed as an overpressure safety device under U.S. Department of Transportation, Pipeline Safety Regulations, Hazardous Liquids Part 195, paragraph 195.428, the subsystem includes the pressure surge relief valve like plug axial pressure surge relief valves, those valves are widely used in the pipeline protection from pressure surge and constructed with main three functions; sensing, tracking and releasing, the plug axial pressure surge relief valves have two types, a gas loaded and a pilot operated configurations, the gas loaded pressure surge relief system has a fast response time about 250 millisecond, but it is equipped with external energy resources like pressurized bottle nitrogen, pressure regulator, check valve, tubing, insulated plenum bottle and control boxes, but the system has lower reliabilities at both component levels as well at system levels, the conventional releasing subsystem not only reduce a system reliability, but also has high operation cost to remain the set pressure with high cavitation and erosion damages, while the pilot relief system is operated by internal fluid energy with a compact pilot, but it has pressure sensing functions and slow response time about two second or more and is less tolerated with dirty fluid and unreliable, every pressure releasing can cause 10 to 30% pressure or energy loss, but U.S. Department of Transportation, Pipeline Safety Regulations, Hazardous Liquids Part 195, paragraph 195.428 did not address redundancy issue, what if there were two pressure relief valves in the Olympic Pipe Line or Piper Alpha platform, the accidents could be avoided?

The conventional valve actuation systems are divided into three types, pneumatic, hydraulic and electrical systems in term of power systems, they are relatively mature for conventional applications, the conventional most fail-open and or fail-closed actuations are powered by springs as spring returns without monitoring devices, but for some challenging applications or server services like fast pressure protection less than one or two seconds or remote pipelines or pumping stations or compression stations and subsea drilling and production, offshore platform operation and subsea drilling and production or safety protections, the conventional valve actuation system just cannot meet the challenges, the first is the speech for isolating or releasing, time is life and money for each accident, the second is reliable power source availability, without electricity, how the modem computer driven control system would works, the third is safety issue for most cylinder assembly joint, they are equipped with long external bolts for containing pressure, the bolts are under constantly corrosion and tension either above water or underwater, the corrosion and creep can cause the cylinder assembly to fall apart and can kill the operators, on the other hand, for the actuation power supply, the gas over oil actuators is the current solution, the gas over oil actuator has a pneumatic-hydraulic-electric actuation combining system and is very expansive and larger and less reliable, some of them conventional valve actuation system powered by natural gas cause some environment issues, while the conventional valve actuation system used for subsea applications are equipped by other type of gas over oil actuators for safety valves or BOP applications, in fact the BOP is just other type of block valve, this system is powered by a group pressurized nitrogen bottles, finally the actuator installation is other issue, most valve is need to equipped with actuator to operate, but one time consuming process is to adjust a position between the valve shaft and the joint flanges, in short those systems are inefficient, unreliable and expensive, for example a 3000 psi pressurized bottle nitrogen on the land would become less than 1500 psi gas due to the deep water pressure and the deep water temperature and the actuation system is not reliable, what if there was a Deadman's switch in the BOP actuation system, the Deepwater Horizon accident could be avoided?

In short, the current solutions do not work efficiently and reliably, what are missing for all existing specifications or solution? What if there is no electric power for signal transformation or actuation! How many redundancy is needed for worst-case scenario or a failure mode, what is the speech of isolating or releasing with current technology? So the industry has long sought means of improving the performance of the pressure protection valve and the actuation systems enabling the valve to handle various flows under multiple extreme conditions.

In conclusion, insofar as I am aware, no such a system is formerly developed with versatile seal ring assembly, hybrid highly reliable pressure protection system, easy manufacturing at lower cost, they can be used for blocking and releasing overpressure fluids in critical services with the highest reliability.

SUMMARY

This invention provides a disrupt innovation, a novel systematic actuation solution for the hybrid High Integrity Pressure Protection System instead of the conventional valve/actuator/sensor solution at a component level. In the system there is no relief valve or bock valve, but a pressure control actuation system to release or block over-pressurized fluid in a hybrid manner, the thermal actuators are embedded in the hybrid high integral pressure protection system for critical services or under extreme conditions even without electricity or external power supply, the thermal actuator is based on thermodynamics (ideal gas law with three basic elements pressure, volume and temperature (heat)). This hybrid pressure protection system combines relief and block functions in one unit and not only release overpressure fluid into lower pressure zone but also isolate overpressure fluid from normal pressures zone with novel thermal actuators and simple normal open and normal closed valves, this system greatly reduce total executing time and increase reliability with at least two redundancies, the block subsystem has a normal-open, standard pressure class valve integrated with the thermal actuation system and has the isolating time less than 2 second without damaging seat and shaft seal packing, the releasing subsystem has a normal-closed, standard pressure class valve integrated with the thermal actuation system and has the releasing time less than 2 second without damaging seat and shaft seal packing, the system with redundancy feature for the valves and the actuators include at least two pressure sensing devices, combination of blocking and relief at the same time greatly reduce the system cost and has the highest level of system reliability over all prior arts or existing products.

Accordingly, besides objects and advantages of the present invention described in the above patent, several objects and advantages of the present invention are:

(a) To provide high redundant pressure protection system, such a system has the highest system reliability for critical services or extreme conditions. (b) To provide a universal thermal actuator based on thermodynamics, so such an actuator can be operated with multiple supply sources like hydraulic, pneumatic or electric powers, the system can operated in a remote area or under water condition with the highest actuation output or functions in an emergency as a Deadman's switch. (c) To provide a universal actuator, so such an actuator can be operated in the double acting or single acting with air returned reservoirs without sucking any unfillet air and spring loaded forces, so it can prevent corrosion in internal actuation and any risk of unload spring set during assembling and disassembling. (d) To provide a control system, such a system can be used for controlling a normal-open valves as block valves and normal-closed valves as well relief valves, it has a fast response time and releasing time, even if it is out of power and it acts like Deadman switch. (d) To provide a pressure protection system, so the system last 25 year service and fire safety service, the maintain period would increase at least five year period and reduce the operation cost and increase reliability. (e) To provide an actuators system with reliable full stroke test, so the actuator system can be tested for full stroke without any blind spots, more importantly the full stroke test can be taken for the actuators while the valves are still in operation conditions, so the whole H-HIPPS would become really “high integrity” system, so the valve can actuated fast to closed or open for blocking and release over pressurized flow. (f) To provide versatile actuators power supplies, so the valve can actuated with hydraulic, pneumatic, solar and electrical power supply or manual or diver interface under subsea operation or remote pipeline, such connection not only reduce the air pollution but also increase reliability. (g) To provide reliable and environment safe power supply, the actuation system is no long needed to use the pressured natural gas or oil or water as power supplies.

g) To provide reliable and safe pressure vessel joint, such a joint can prevent catastrophic failure of pressure vessel under severe conditions, the actuation system is safe to be used.

Still further objects and advantages will become apparent from study of the following description and the accompanying drawings.

DRAWINGS

Drawing Figures

FIG. 1 is an exploded, quarter cut view of a pressure protection system constructed in accordance with this invention.

FIG. 2 is an exploded, quarter cut view of a thermal actuator of FIG. 1

FIG. 3 is an “A” detail view of valve of FIG. 2

FIG. 4 is a “B” detail view of valve of FIG. 2

FIG. 5 is a front view of power supply assembly of FIG. 2.

FIG. 6 is a cross sectional view of supply assembly of FIG. 5 along line A-A.

FIG. 6a is a “H” detail view of valve of FIG. 6.

FIG. 7 is a cross sectional views of supply assembly of FIG. 5 along line B-B.

FIG. 8 is a top view of an entry shutter control valve of FIG. 2.

FIG. 9 is a cross sectional view of valve of FIG. 8 along line G-G.

FIG. 10 is an ISO view of shutter of FIG. 9.

FIG. 11 is a front view of a linear moving actuator assembly of FIG. 2.

FIG. 12 is a cross sectional view of actuator assembly of FIG. 12 along line H-H.

FIG. 13 is a “M” detail view of the assembly of FIG. 12.

FIG. 14 is an ISO view of an eccentric plug assembly of FIG. 13

FIG. 15 is a “L” detail view of the actuator assembly of FIG. 12.

FIG. 16 is a top view of a shutter valve assembly of FIG. 12.

FIG. 17 is a cross sectional view of the shutter valve assembly of FIG. 16 along line G-G.

FIG. 18 is an ISO view of a shutter of FIG. 17.

FIG. 19 is a top view of two of the shutter valve assembly of FIG. 16

FIG. 20 is a cross sectional view of the valve assemblies of FIG. 19 along line D-D.

FIG. 21 is a front view of actuator base of FIG. 2.

FIG. 22 is a cross sectional view of the actuator base of FIG. 21 along line F-F.

FIG. 23 is an ISO view of a rotor assembly of FIG. 22

FIG. 24 is a “K” detail view of the actuator of FIG. 21.

FIG. 25 is a cross sectional view of the actuator base of FIG. 21 along line J-J.

DESCRIPTION

FIG. 1 illustrates a pressure protection system 10, the system 10 has an isolating subsystem 20′ and a releasing subsystem 20 constructed in accordance with the present invention, the system 10 has an inlet 30, an outlet 30′ and release port 30″ and sensing sections 24, the isolating subsystem 20′ has a normally open valve 35′ coupled with a thermal actuation subsystem 50 for isolating flows from the inlet 30′, the thermal actuation subsystem 50 has a sensing section 54 connected with a sensing section 24 for sensing incoming flows from the inlet 30 (a tubing not shown), the releasing subsystem 20 has a normally closed valve 35 coupled with a thermal actuation subsystem 50 for releasing flows into the releasing port 30″ from the inlet 30, the thermal actuation subsystem 50 has the sensing section 54 connected with the sensing section 24 for sensing incoming flows from the inlet 30 (a tubing not shown).

Referring FIGS. 2-4, 8, 9 the thermal actuation subsystem 50 has a power supply assembly 180, a base actuator 100 and a control chamber assembly 183 with a safety valve 196 for on land applications, the power supply assembly 180 has a compressor 181 and a fluid pad assembly 143 with an intake shutter valve 144, a tubing 195 for supplying fluid powers, the base actuator 100 has a rotary drive assembly 170 and three linear drive assemblies 101 to actuate the rotary drive assembly 170, the rotary drive assembly 170 has a link groove A and a link groove B, a link hole A connected with the groove A and a link hole B connected with groove B, the fluid pad assembly 143 has an inlet port A and an outlet port B and the intake shutter valve 144 disposed between the port A and the port B, the port A is connected with the compressor 181 through the tubing 195 and expanding to the link groove A, the port B is connected with link groove B and a link hole B, the intake shutter valve 144 has a hole 145 connected with the inlet port A, a hole 146 connected with link groove B, the intake shutter valve 144 has a front closed/back open position under low pressures or no pressure of the fluids from port A, a front open/back open position under high pressures of the fluids from port A, the linear drive assembly 101 has a cylinder assembly 135, a piston assembly 139 movably disposed in the cylinder assembly 135, the piston assembly 139 and cylinder assembly 135 are forming a cavity A and a cavity B, an air reservoir 102 and a front plate assembly 125 defining Cavity AA, the linear drive assembly 101 also has a side port 142, a front plate assembly 125, a pair of composite tubing A and tubing B respectively connected Cavity AA and Cavity B, the composite tubing A and tubing B are made out of nonmetal of one end for seals and metal for the rest structures, tubing B has an nonmetal end connected with the back plate assembly 141, the piston assembly 139 with a piston 140 and a back plate assembly 141, the front plate assembly 125 has bores 127 and 126 respectively connected with the cavity B and Cavity A with nonmetal of the composite tubing A for sealing, so nonmetal end joints provide the seals as well as strengths for high pressure applications and smoothly fast operations and long service, an internal shutter valve 104 placed between bore 126 and bore 127, the internal shutter valve 104 has a front closed/back open position under low or no pressures and a front open/back closed position under high pressures, when high pressurized fluid from power supply 180 flows into hole 145, the Port A and push the intake shutter valve 144 to the front open/back open position, the pressurized fluids get into the link groove A into cavity A through side port 142 for actuating the piston assembly 139 outward, while fluids in the cavity B is releasing through tubing B, link port B, link groove B and pass the intake shutter valve 144 through the hole 147 and hole 146 are connected through passages 153 into port B, while the pressurized fluid get into bore 126 in the front plate assembly 125 and through the tubing A and pushes the internal shutter valve 104 to the front open/back closed position, so the high pressurized fluid get into cavity AA in reservoir 102, when the high pressurized gas against line pressures fluid from sensing section 24 is reaching at a preset limit, the center shutter valve 196 is releasing the actuation fluid under subsea applications or the safety valve 196 is open in land applications, the pressure in tubing 195 comes near zero, the intake shutter valve 144 move back at a front closed/back open position, hole 147 and hole 146 are blocked to the port B, the internal shutter valve 104 moves back to a front closed/back open position, so hole 105 is disconnected with bore 126 and hole 107, hole 106 is connected with hole 107 and bore 127, so the pressurized fluid in cavity AA flows into cavity B and push the piston assembly 139 moves inward as a function of air return instead of conventional spring return, while a three-way solenoid valve (not shown) may be used on the fluid pad assembly with the internal shutter valve 104 for the same function as well.

Referring FIGS. 5-7, the compressor 181 has an outlet 182 connected with the control chamber assembly 183, the control chamber assembly 183 has a housing 184 and a piston assembly 187 movably disposed in the housing 184 separating the housing 184 into an active cavity 191 or a center air reservoir and a sensing cavity 192, the housing 184 has a large bore 185 and a small bore 186, the inlet sensing port 54, an outlet port 193, the piston assembly 187 has a bore 109 a expanding a bore 110 a, the center shutter valve 194 disposed in the bore 110 a, a large OD 189 engaged with the large bore 185 and a small OD 188 engaged with the small bore 186 for sensing and balancing pressures between cavity 191 and cavity 192 by a preset ratio between an area of the large bore 185 and an area of the small bore 186, the cavity 191 has a pressure sensor 197 and the pressure safety release valve 196 for sensing and releasing pressures in cavity 191 when the pressures in cavity 192 reach a preset value over preset pressure, the center shutter valve 194 for releasing over pressures has a body 145 a with multiple releasing ports 148 a for releasing flows without causing cavitation and a shutter bore 149 a, a shutter assembly 151 a disposed in the shutter bore 149 a, a front seal ring 158 a, a back adjustable seat 159 a and, a spring 160 a biased between the shutter 151 a and the back adjustable seat assembly 161 a, the shutter assembly 151 a has a center hole 152 a extending to multiple radial holes 157 a and a head 154 a against the seal ring for front seals and the head 154 a can be constructed with an extended tip like intake shutter valve 144 and acts like a limit switch as well when the piston assembly 187 moves up and down in the active cavity 191 as a Deadman switch, the cavity 191 has a position sensor 198 to sense a position of the piston assembly 187 under pressure and has two ports 54 in the sensing cavity 192 respectively connected with the piping sensing sections 24 (tubing not shown) and pressure sensor 197.

Referring FIGS. 8-10, the intake shutter valve 144 has a body 145 a having a bore 149 expanding to bore 150, the hole 145, a shutter 151, a back adjustable seat 161 and a back seal ring assembly 159 disposed between the shutter 151 and back adjustable seat 161 with a curve surface 162 for seals, a spring 160 biased between the shutter 151 and the back seat 161 for creating a preset pressure, the shutter 151 has a head 152, a center hole 156 expanding to multiple side holes 153 and multiple back slots 155 for releasing flows without cavitation damages and a back seal surface 157, the head 152 has an extended tip with a seal ring 154 for creating full piston effect between front pressures and the spring 160, a curve seal surface against the front seal 158 for seals between 149 for sealing between the hole 147 and the bole 146, the shutter 151 with the extended tip can be actuated by pressures or a manual, magnetic force or stopped by a hard stop, the body 148 has three holes 145, 146 and 147.

Referring FIGS. 11-15, the linear drive assembly 101 can be used as a linear actuator and has a front plate assembly 126 having a front lock groove 138 defined by a conical surface 129 and three radial holes 137 and an air reservoir assembly 102 and a back plate assembly 141 with a side hole 142 and a back step to preventing the back plate assembly from separating with the piston assembly 139, the air reservoir assembly 102 has an electric heater assembly 103 for heating air in the cavity AA in order to increase gas pressure, the front plate assembly 125 has three radial thread hole 124 respectively receive three setscrew 199 through radial holes 137 for securing joints between the cylinder assembly 135 and the front plate assembly 125, the front plate assembly 125 has three bore 128 respectively expanding three moon-shape side slots 129 and three eccentric lock plug assembly 130 respectively inserted into bore 128, lock plug assembly 130 disposed in the bore 128 has a plug 131 with two slots 132 and three C shape spring rings 130 inserted from side slots 122 into the slot 129, as the plug assemble 130 is rotated clockwise, so the front plate assembly 125 can be inserted into the cylinder assembly 135, then as the plug assemble 130 is rotated anticlockwise back, the three C shape spring ring 134 are engaged with the lock groove 138 for securing joints between front plate assembly 125 and cylinder assembly 135, so the redundant locking devices further secure the front plate assembly 125 and cylinder assembly 139, so the linear drive assembly 101 has a flexible back joint with the back plate assembly 141 and a rigid joint with front plate 126 to compensate any misalignment between the rotary drive assembly 170 and the linear drive assembly 101 as well over pressure relief from the back plate assembly 141 and thermal expansion without weakening bolts joint.

Referring FIGS. 16-20, the internal shutter valve 104 has a body 108 having a bore 109 expanding to a bore 110 and hole 105, a shutter 111 and back a seal ring 120 and a back seal ring 117 movably disposed in the bore 109 and a back adjustable seat assembly 121 with a seal surface 122 engaged with the back seal ring 119 at a back closed position and a spring 165 biased between the shutter 111 and the back seat 121 for creating a preset pressure, the seal ring 120 between the bore 109 and shutter 111 for generating a piston effect against the spring 165, the shutter 111 has a head 116 with a curve front seal surface, a center hole 114 expanding to multiple side holes 112 and to multiple back slots 115, a back seal ring 117, the body 108 has three holes 105, 106 and 107, the valve 104 has a front seat 118 placed in the bore 109 against the head 116 for seals between the hole 110 and the hole 107, finally two the internal shutter valves 104 are connected as a counter-balanced valve 169 which is used in hydraulic systems working with overriding (running-away) or suspended load and is designed to create backpressure at the return line of the actuator to prevent losing control over the load.

Referring FIGS. 21-25, the base actuator 110 has the rotary drive assembly 170, the rotary drive assembly 170 has two positioner sensors/controlling 172 in an opposite direction or 180 degree apart and a rotor assembly 172, the rotor assembly 172 has two stops 173,173′ 90 degree part to respectively engaged with the positioners 172,172′ for sensing a position of the rotor assembly and controlling as the rotor assembly is rotated clockwise and anticlockwise, the rotary drive assembly 170 has three relative position adjustable assemblies 178 respectively located between flange assemblies 171 and body 171 a for adjusting a relative position between the flange assemblies 171 and the rotor assembly 172, each of relative position adjustable assemblies 178 has a slot 174 on the body 171 a and a screw set 175 with a screw and lock washers through the slot 174 into the flange assembly 171 for adjusting and securing a relative position, a setscrew hole 176 and the setscrew 177 inserted in the hole 176 penetrated into high friction structure on the body 171 a, the high friction structure can be high friction coatings, or dents, knurling surfaces or high frication material rings is respectively embedded in the body 171 a under screw sets 175 for securing a positions as a redundant beside the position lock fastener assembly, so even under fast cycles operation or vibration, the relative position between the flange assemblies 171 and the rotor assembly 172 would change with the adjustable device assemblies 178 with +1-20 degree, but the absolute travel range (0-90) of the rotor assembly 172 would never change, the relative position adjustable assemblies 178 would greatly save setting times on the fields.

Conclusions

The present invention provides a long sought solution—a reliable, powerful and safety, efficient power supply for pressure protection or valve actuation in any location, the thermal actuator is not a conventional related temperature base rather thermodynamics base, the ideal gas law, it applies all three basic elements (a) pressure (b) volume (c) heat to actuate a flow control system, the modern pneumatic and hydraulic actuation systems have over 100 year history, but there is no system so far with full three thermal elements as clear as this system to define a thermal actuation system, the fundamental difference between the conventional actuation system and this thermal actuation system is how to deal with three elements, pressure, volume and heat, the heat in the conventional actuation system is a form of energy waste, while the heat in this thermal actuation system generated by compressor, weather or heat tracing is a form of useful energy to increase the air pressure, so any heat form would help this thermal actuation based on all three basic thermodynamics elements (a) pressure (b) volume (c) heat, even with the conventional compressor, the outputs is about 80 to 150 psi, but with the elevated temperature by electric tracing or natural weather, the pressure can go up to 13.5 to 50% (pressure), so with large volume of the air reservoir (volume) and heated elevated temperature of air (temperature), even without an input air supply line, the actuator can performance like a double acting actuator, moreover the thermal actuation system with a solar power systems can be independently used without any conventional air supply, natural gas or hydraulic or electric power supplies or with conventional air supply or AC electrical power line as a standby power supply, finally the air supply source can be a portable air compressor or pressure supply line, the power supply source for the compressor can be AC power line or solar power, the air reservoir can be located at linear drive unit or center unit, the heat source, for subsea applications, a volume vessel with a heat system and insulation layers would be added to the conventional actuation system between the actuation system and the group of pressurized nitrogen bottles and would greatly increase pressure.

The control chamber assembly is the brain of the system in this invention, it combines all control elements, pre-set condition, sensing and judgment seamlessly as one unit at the highest level of adaptability and controllability for most control applications like the level control as the sense piston move up and down as a liquid level increase or decrease in the sensing cavity, or temperature control, as a temperate change in the sensing cavity, the piston can move up and down, or motion control and so on, the control chamber assembly is based on two human brain function with two systems; high level of control of the cerebrum system and a low level control of the cerebellum system, at the cerebrum system, the control chamber can make decision either to release, restore or block the line pressure and acts with or without electric signal or power and with a self-feedback function from the line pressure, while at the cerebellum system, it check the set pressure in the activity cavity against the line pressure in the sensing cavity with the center shutter valve, safety valve, the pressure sensor as redundant devices, at the low level of control, the valve functions become simpler and is no longer to define a block valve or relief valve, just simple normal closed and normal open valves, it integrates this pressure protection system at the lightest level of reliability, simplicity and lowest level of barrier over all exiting pressure systems in the market or in research and over all prior arts, while electronic sensor, digital control, wireless communication devices still can be added on this system to communicate with other devices or human through buses like profit-bus, foundation bus or wireless communication, the control chamber system can be used for both linear or rotary actuation system and subsea BOP or valve or tree/well flow or pressure controls, so there is no block or release but release/block actuator, only single control chamber system, it not only increase integrity of protection system, but also simplify the valve design and selection and eliminate the partial stroke testing, by switching functions between normally open positions to normally closed in the two valves with full stroke test and increase the reliability.

The shutter valves is the heart of the system in this invention to keep the fluid running in proper directions and react to the line pressure changes fast and precisely with the self-control, safe manner, without the shutter valves or the control chamber, the High Integrity Pressure Protection System would not be truly created. The innovative shutter valve has a novel shutter, it has a conical or spherical head with seal surface against the front seal and back seal ring, conical or spherical back seat and biased by a spring and a center fluid passage instead of external fluid passage, so the shutter valve with double balanced seats unlike any other directional control valves spool or shear seal, it overcomes inherent radial spool sealing jamming or leakage due to erosion or cavitation, or high pre-stressed flat shear seal valve with high cost due to process, self-centering conical seal from both ends would keep the shutter either front seal or back seal, since the front porting and back porting are locate evenly around the shutter, any open closed operation would not cause unbalanced wearing or reaction forces, while the middle groove with seal rings would prevent any possibility of inlet and outlet connection during transitions for some applications and creating full piston effect, moreover multiple middle grooves without the seal rings or with less friction of seal rings can help shutter move evenly faster for some application requirements, also the hollow shutter not only reduces the shutter Inertia with less weights but also stabilizes the movements of shutter with a larger OD engaged surfaces especially for fast cycle operations and is easily to control the directions of shutter between forward or backward movements, in other hand, the changeable ratio between the opening area and closed pressure area make speed control much easy and pressure release time and reseating time shorter, moreover the shutter with the extend tip can be actuated by a front pressure or acts like a limit switch in many applications like the control chamber as the piston assembly moves up, finally the shutter valve has multiple control functions (a) front open, back closed positions (2) front closed/back open positions (3) front open/back open positions and (4) a two-shutter valve combination become a counterbalanced control valve used for many hydraulic fluid control applications (5) a limit switch or manual switch for controlling flow instead of trigging by pressures.

The present invention discloses other breakthrough achievement—the air return mechanism instead of spring return, the air return mechanism with the shutter valve not only does increases output force or torques without decreasing air acting forces, unlike the conventional spring return mechanism, which share the acting force about 40% and 10% converting loss from total capacity 100% of double acting forces or torque but also eliminates the spring return sets which is heavy, big and expensive and porn to corrosion with breath air holes, furthermore there is no entry of unfilled air into the actuator or air reservoir other than air supply, so no corrosion or particle would damage the actuator cylinder or air reservoir, more importantly the air return mechanism is constantly monitored by air pressure gauge and ready to act at any moment with the highest level of reliability, while spring set return is not constantly monitored, it can be weaken or corroded without any information of its condition for over time, under some working conditions like hot temperature, high humility or offshore platform, the air return reservoir can perform well at the designed condition for long service, where the spring return may not work well due to spring corrosion, creeping, finally the air return reservoir can be installed at any position, vertical, horizontal and between and with other actuators linear actuator, rack and pinion or vane actuators, there is no material fatigue issue, finally hot weather can help air return reservoir perform better without increasing heating cost or solar power consumption with heat absorbing material or dark color coating on the cylinder to increase pressure of the air on the reservoir or it can be added insulation layers and internal heater for cool weather locations or subsea as well, finally it is very suitable for earthquake area or high vibration applications, most actuators with spring return mechanisms are unbalanced, if with net spring set, the matter even gets even worse, so the actuators may not even survive, to preform is out of question.

The operational innovation features are long waiting solutions and include (1) the cylinder joint method with a rigid joint between the font plate assembly and the cylinder assembly with the novel locking device and a flexible joint between the back plate assembly and the cylinder assembly with the back step, the rigid front joint with the eccentric plug assembly and radial locking setscrew provide simple and antic corrosion robust locking mechanism, since the bolts are defined as a pressure container part in the pressure vessel standards around the world, according to Navy and major marine structures specifications, all vital bolts should be made out of Inconel alloy in order to prevent catastrophic failure due to corrosion where the seat water corrosion is a major problem, moreover this requirements not only greatly increase cost for the marine projects, but also create compatibility problem with surrounding parts like washer, nuts and welding areas, thanks to those novel joint method, there is no bolts on the cylinder assembly as pressure containing part parts even with setscrews, so the feature provides a redundant locking function, moreover there is no tension bolts in the rigid joint and the flexible joint, so even temperature change would not affect the joint seal with the back step, while the cylinder assembly with thermal expansion would not affect joint seal as well, meanwhile they are easy to assembly and disassembly and can stand for high cycle operations like high cycle relief application without retightening bolts and increase reliability and reduce the cost, as a result the linear drive assembly eliminate any joint leak or break due to those thermal expanding, the back joint with axial freedom successfully solves the creep issue for most pipelines and offshore applications (2) the porting system, most external tubing on the conventional actuator are constructed like spaghetti and can easily be hit and damaged, corroded and mislaid out, but this porting system with two porting systems A and B not only reduce tubing leak by accident hit during the operation and transportation and reduce the pollution if the naturel gases are used for actuation power supply, but also simplify porting tubing layout, the composite tubing A, B not only solve the corrosion issues but also balances load on the piston assembly, the nonmetal end of the tubing A can be secured with the front plate assembly for seals and joint and an open end connected with cavity A, the tubing A can be secured with front plate assembly to additional external outlet outside the front plate assembly for accelerating or deaccelerating open or closed speeds with multiple fluid pads for fast closing or opening less one second without damaging valve seat and stem packing by operating step opening or closing, three or two ports at the beginning and one or two ports at the closed position or vice versa, in offshore platform where the working space is very limited, so the internal tubing not only provides safe and secure flow line, but also have the shortest flow line and provide a multiple flow line for each piston, which not only have more flexible control with multiple fluid pad assemblies, so for quick closing operation, at beginning, three flow lines can be opened and in the end, only one flow control is set to open and reduce the impact force on the seat or packing of valves (3) the relative position adjustment is a great feature for most operators in the field, the conventional positions adjustment is based on a absolution positions change between 0-90 degree, while the relative position adjustment mechanism separating from the conventional absolute position adjustment is other disrupt innovation in this invention, for most operators in the field, a correct closed position of closure members like disc, ball or plug is critical for all rotary valve, even 0.5 degree off can cause leak, but 99% of stem position adjustments are about the stem relative position to the joint flanges bolt holes with no need to alter a factor set range 0-90+/−0.5 degree, only 1% of the actuation adjustments is an absolute adjustment between 0-90+/−5 or 10 degree, the relative positions adjustments on the rotatable interface plates is a simple solution to 99% problems, for further position security, anti-loosening washers or semi-permanent adhesive may be added with the bolts after setting a correct position, moreover the high friction structures with the setscrews is designed to secure the adjusted position as a redundancy, for 1% problems, the factory set 90+/−5 can be solved at the factory, it along saves 60% time in most rotary actuations installation, moreover the top and bottom flange assembly can be interchangeable, so without changing the design or installing the cylinder assembly, the direction of rotations of actuator can changed from clockwise to anticlockwise, or for any valve connection without body change especially in field repairs.

Without the high integrated thermal actuation system, the High Integrity Pressure Protection System would not be truly created, the currant pressure protection systems have many problems like unbalanced actuation system which is the inherent problem for the most actuators in the market, the actuation systems without protection device from excessive torsion or unbalanced or loosened joints between actuators and valve account for 80% valve seat or packing failures, so far no single valve or actuator manufacture recognize that, the universal thermal actuation system in this invention is a synergic improvement from two prior patents and is to aim to disrupt current solutions and improve the power supply efficiency and diversity and the overall performances by modularizing and equipped with the base actuator and the control chamber and valves.

Although the description above contains many specifications, these should not be construed as limiting the scope of the invention but as merely providing illustration of some of the presently preferred embodiments of this invention.

Thus, the scope of the invention should be determined by the appended claims and their legal equivalents, rather than by the examples given. 

I claim: 1) A fluid control system comprising: (a) A piping assembly having an inlet section and an outlet section connected with a pipe and at least one release section and at least one sensing connection. (b) A hybrid pressure control assembly has at least one pressure-isolating subsystem and at least one pressure-releasing control subsystem, said subsystem has at least one valve and at least one actuation system, said actuation system has at least one pressurized power source, at least one volume vessel and at least one heat source, said pressurized power source has one of a plurality of forms including a pressurized fluid supply line and a compressor, said compressor is powered by one of a plurality of forms including AC power lines, DA power lines and solar power units, said volume vessel includes one of a plurality of forms including a local volume vessel and a center volume vessel, said heat source has one of a plurality of forms including a solar heat, an electric heater, a gas heater, a steam heater and a fire burner, said thermal actuation system also has a control chamber assembly, at least one fluid pad assembly and a base actuator assembly. 2) The fluid control system of claim 1, wherein said control chamber includes a pressure vessel having an active cavity assembly and a sensing cavity assembly and a piston assembly, said sensing cavity assembly is connected with said sensing connection, said actively cavity assembly is connected with said pressurized power source and said fluid pad assembly, said piston assembly has an active piston and a sensing piston respectively, movably engaged with said actively cavity assembly and said sensing cavity assembly for controlling a ratio between pressures in said active cavity assembly and pressures in said sensing cavity assembly at a preset condition, said active cavity assembly also includes a safety valve, a pressure sensor and a position sensor and a pressure relief valve with a limit switch. 3) The fluid control system of claim 1, wherein said thermal actuation system includes at least one shutter valve, said shutter valve has at least one inlet port and one outlet port, a body assembly, a shutter assembly movably disposed in said body assembly and an adjustable back seat assembly and a set of spring biased between said shutter assembly and said adjustable back seat assembly, said adjustable back seat assembly has a head defined by one of a plurality of forms including conical surfaces and spherical surfaces, said body assembly has a body having a shutter bore extended to a front hole and a back bore and a front seal ring assembly disposed between said body assembly and said shutter assembly for front seals and a back seal ring assembly disposed between said adjustable back seat assembly and said shutter assembly for back seals, said shutter assembly has a seal ring, a shutter disposed in said shutter bore having a head, a center hole extended to front multiple radial ports and a back end defined by multiple fluid slots and a back sealing surface against said back seal ring assembly for seals, said back sealing surface has one of a plurality of configurations including conical surfaces and spherical surfaces, said head has one of a plurality of configurations including (a) an extended tip with a seal ring and a front sealing surface against said front seal ring assembly for providing front seals (b) a front sealing surface against said front seal ring for providing front seals, said front sealing surface has one of a plurality of forms including conical surfaces and spherical surfaces. 4) The fluid control system of claim 1, wherein said base actuator assembly has a rotary drive assembly and at least one linear drive assembly and a porting system, said rotary drive assembly has a rotator assembly and a porting system, a body assembly and two flange assemblies at least one relative position device assembly for controlling relative positions between said flange assembly and said rotator assembly, said relative position device assembly has a slot, a friction ring and screw hole on said body assembly and a setscrew hole on said flange assembly and a fastener assembly having inserted into said slot and the screw hole for locking and unlocking a position and a setscrew screwed into said setscrew hole penetrated into said friction device on said body assembly against said flange assembly for locking said relative positions, said friction device has one of plurality forms including coatings, knurling surfaces, dents, a solid ring embed into said body assembly under said setscrew, said rotary drive assembly also has two position sensors for monitoring positions of said rotary shaft. 5) The fluid control system of claim 4, wherein said linear drive assembly has a front plate assembly and a back plate assembly having a back step and a cylinder assembly axially restricted by said back step and placed between said front plate assembly and said back plate assembly and a piston assembly movably disposed in said cylinder assembly, an air reservoir assembly installed with said front plate assembly and at least one lock device assembly between said cylinder assembly and said front plate assembly, said lock device assembly has a conical groove on said cylinder assembly and a radial screw hole through said cylinder assembly into said front plate assembly, a radial slot to expanding to an axial hole on said front plate assembly and a setscrew threaded into said front plate assembly through said through said cylinder assembly for securing joints between said front plate assembly and said cylinder assembly, said lock device assembly also has a plug assembly disposed between said front plate assembly and said cylinder assembly for securing joints between said front plate assembly and said cylinder assembly, said eccentric plug assembly has a plug having two flat surface inserted into said axial hole and a set of spring washer having a slot to receive said plug through said radial slot engaged with said flat surfaces and said conical surface of said groove on said cylinder assembly for locking and unlocking between said front plate assembly and said cylinder assembly, 6) The fluid control system of claim 4, wherein said porting system has a porting B subsystem and a porting A subsystem, said porting B subsystem has a port B connected with a composite tubing B in said back plate assembly through a link groove B, said composite tubing B has a seal nonmetal end constructed with said back plate assembly and a metal housing connected with a cavity B through said piston assembly, said porting A subsystem has a port A connected with a link groove A to a cavity A to a composite tubing A, said tubing A has a metal housing and a seal nonmetal end constructed with said front plate assembly for connecting between said cavity A and a cavity AA through said shutter valve. 7) A thermal actuation system has at least one pressurized power source, at least one volume vessel and at least one heat source, said pressurized power source has one of a plurality of forms including a pressurized fluid supply line and a compressor, said compressor is powered by one of a plurality of forms including AC power lines, DA power lines and solar power units, said volume vessel includes one of a plurality of forms including a local volume vessel and a center volume vessel, said heat source has one of a plurality of forms including a solar heat, an electric heater, a gas heater, a steam heater and a fire burner, said thermal actuation system also has a control chamber assembly, at least one fluid pad assembly and a base actuator assembly. 8) The thermal actuation system of claim 7, wherein said control chamber includes a pressure vessel having an active cavity assembly and a sensing cavity assembly and a piston assembly, said sensing cavity assembly is connected with said sensing connection, said actively cavity assembly is connected with said pressurized power source and said fluid pad assembly, said piston assembly has an active piston and a sensing piston respectively, movably engaged with said actively cavity assembly and said sensing cavity assembly for controlling a ratio between pressures in said active cavity assembly and pressures in said sensing cavity assembly at a preset condition, said active cavity assembly also includes a safety valve, a pressure sensor and a position sensor and a pressure relief valve with a limit switch. 9) The thermal actuation system of claim 7, wherein said thermal actuation system includes at least one shutter valve, said shutter valve has at least one inlet port and one outlet port, a body assembly, a shutter assembly movably disposed in said body assembly and an adjustable back seat assembly and a set of spring biased between said shutter assembly and said adjustable back seat assembly, said adjustable back seat assembly has a head defined by one of a plurality of forms including conical surfaces and spherical surfaces, said body assembly has a body having a shutter bore extended to a front hole and a back bore and a front seal ring assembly disposed between said body assembly and said shutter assembly for front seals and a back seal ring assembly disposed between said adjustable back seat assembly and said shutter assembly for back seals, said shutter assembly has a seal ring, a shutter disposed in said shutter bore having a head, a center hole extended to front multiple radial ports and a back end defined by multiple fluid slots and a back sealing surface against said back seal ring assembly for seals, said back sealing surface has one of a plurality of configurations including conical surfaces and spherical surfaces, said head has one of a plurality of configurations including (a) an extended tip with a seal ring and a front sealing surface against said front seal ring assembly for providing front seals (b) a front sealing surface against said front seal ring for providing front seals, said front sealing surface has one of a plurality of forms including conical surfaces and spherical surfaces. 10) The thermal actuation system of claim 7, wherein said base actuator assembly has a rotary drive assembly and at least one linear drive assembly and a porting system, said rotary drive assembly has a rotator assembly and a porting system, a body assembly and two flange assemblies at least one relative position device assembly for controlling relative positions between said flange assembly and said rotator assembly, said relative position device assembly has a slot, a friction ring and screw hole on said body assembly and a setscrew hole on said flange assembly and a fastener assembly having inserted into said slot and the screw hole for locking and unlocking a position and a setscrew screwed into said setscrew hole penetrated into said friction device on said body assembly against said flange assembly for locking said relative positions, said friction device has one of plurality forms including coatings, knurling surfaces, dents, a solid ring embed into said body assembly under said setscrew, said rotary drive assembly has two position sensors for monitoring positions of said rotary shaft. 11) The thermal actuation system of claim 10, wherein said linear drive assembly has a front plate assembly and a back plate assembly having a back step and a cylinder assembly axially restricted by said back step and placed between said front plate assembly and said back plate assembly and a piston assembly movably disposed in said cylinder assembly, an air reservoir assembly installed with said front plate assembly and at least one lock device assembly between said cylinder assembly and said front plate assembly, said lock device assembly has a conical groove on said cylinder assembly and a radial screw hole through said cylinder assembly into said front plate assembly, a radial slot to expanding to an axial hole on said front plate assembly and a setscrew threaded into said front plate assembly through said through said cylinder assembly for securing joints between said front plate assembly and said cylinder assembly, said lock device assembly also has a plug assembly disposed between said front plate assembly and said cylinder assembly for securing joints between said front plate assembly and said cylinder assembly, said eccentric plug assembly has a plug having two flat surface inserted into said axial hole and a set of spring washer having a slot to receive said plug through said radial slot engaged with said flat surfaces and said conical surface of said groove on said cylinder assembly for locking and unlocking between said front plate assembly and said cylinder assembly. 12) The thermal actuation system of claim 10, wherein said porting system has a porting B subsystem and a porting A subsystem, said porting B subsystem has a port B connected with a composite tubing B in said back plate assembly through a link groove B, said composite tubing B has a seal nonmetal end constructed with said back plate assembly and a metal housing connected with a cavity B through said piston assembly, said porting A subsystem has a port A connected with a link groove A to a cavity A to a composite tubing A, said tubing A has a metal housing and a seal nonmetal end constructed with said front plate assembly for connecting between said cavity A and a cavity AA through said shutter valve. 13) A shutter valve has at least one inlet port and one outlet port, a body assembly, a shutter assembly movably disposed in said body assembly and an adjustable back seat assembly and a set of spring biased between said shutter assembly and said adjustable back seat assembly, said adjustable back seat assembly has a head defined by one of a plurality of forms including a conical surface and spherical surface, said body assembly has a body having a shutter bore extended to a front hole and a back bore and a front seal ring assembly disposed between said body assembly and said shutter assembly for front seals and a back seal ring assembly disposed between said adjustable back seat assembly and said shutter assembly for back seals, said shutter assembly has a seal ring, a shutter disposed in said shutter bore having a head, a center hole extended to front multiple radial ports and a back end defined by multiple fluid slots and a back sealing surface against said back seal ring assembly for seals, said back sealing surface has one of a plurality of configurations including conical surfaces and spherical surfaces, said head has one of a plurality of configurations including (a) an extended tip with a seal ring and a front sealing surface against said front seal ring assembly for providing front seals (b) a front sealing surface against said front seal ring for providing front seals, said front sealing surface has one of a plurality of forms including conical surfaces and spherical surfaces. 14) The shutter valve assembly of claim 13, wherein two of said shutter valve are constructed as a counter-balanced valve. 